Oil well drilling apparatus



Oct. 20, 1942. A. R. MAIER OIL WELL DRILLING APPARATUS Original FiledJune 15, 1936 5 Sheets-Sheet l INVENTOR: flugasf R. M6?! er ORNEY.

.Oct. 20, 1942. A. R. MAIER 2,299,548

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TT NEY 5 Sheets-She et 3 Oct. 20, 1942. A. R. MAIER OIL WELL DRILLINGAPPARATUS Original Filed June 15, 1 936 QM Q 7 MN Oct. 20, 1942. R MAlEROIL WELL DRILLING APPARATUS Original Filed June 15, 1936 5 Sheets-Sheet4 V .e la a Q 0 mm m mm mm W I mm u $8M m:| a fl Q Q my Q Q J JfiJ JT Nl u n I I W I T i LP? ii MN \IH rm Y: a 2 ms 7 ORNEY Oct. 20, 1942. A.R. MAIER 2,299,548

OIL WELL DRILLING APPARATUS Original Filed June 15, 1 936 5 Sheets-Sheet5 FIIBE.

INVENTQR.

HI'S AT RNEYS Patented Oct. 20, 1942 2,299,548 011. WELL anama APPARATUSAugust R. Maier, Dallas, Ten, assignor to Oil Well Supply Company, acorporation of New Jersey Original application June 15, 1936, Serial No.

85,398. Divided and this application September 7, 1939, Serial No.233,861

(01. comm 3 Claim.

This invention relates to improved control means for a plurality ofengines arranged to be coupled together, and more particularly to acombined steam control and valve gear operating mechanism of thecharacter hereinafter more fully shown, described and claimed.

The present invention is a division of the invention disclosed in myco-pending application Serial No. 85,398, now abandoned. For a morecomplete understanding of the present invention and the novel featureswhich distinguish it from the teachings of the prior art, referenceshould be made to the following detailed disclosure, the accompanyingdrawings, and the appended claims.

In drilling wells, such as oil wells or gas wells, by means of a rotarydrilling apparatus, a vertical drill stem carrying a bit on its lowerend-is rotated about its axis by means of a rotary having a horizontalrotating table through which the drill stem passes and which is squaredto permit the latter to gradually be lowered during rotation. The drillstem is hollow and mud is pumped downwardly through this drill stem intothe bottom of the well and flowing up about the drill stem carries withit the cuttings, which are separated, and the mud returned. The pumpingof the mud and the rotation of the rotary and drill stem occursimultaneously and continue until the top of the squared part of thedrill stem reaches or approaches the rotating table of the rotary. Atthis point the rotation of the drill stem and, the pumping of mudthrough it are stopped and the drill stem is hoisted from the well sothat an additional joint of the hollow stem may be joined below thesquared element which is called a Kelly, whereupon the drill stem isagain lowered until the squared part or "Kelly engages the rotary table.Thereupon the rotation of the drill stem and the pumping of mud areresumed and the stem gradually lowered as the drilling proceeds. Thissequence of operation continues until the well reaches the desired levelor until oil is found or the hopes of finding it are abandoned. As thedrilling proceeds also the well is lined with casing to prevent cave-in,etc.

The hoisting of the drill stem requires a large amount of power, as theweight of the drill stem and associated tools, or of the casing pipewhen the well becomes very deep, is very great; sometimes as much as 300tons. The power required to drive the rotary is relatively very small,as is also the power required to drive the mud circulating pump.Heretofore the same engine has generally been used for driving therotary and driving the hoist. However, the conditions required to supplythe power required for the hoisting mechanism are not such as to favorthe efflciency of the engine through the relatively longer periods whenit is driving the rotary, and the efliciency of the engine is,therefore, very much smaller during the rotary-driving periods thancould be obtained if an engine were used at this period suited to thepower requirements of the rotary. The power requirements for the mudpumps are also quite different from those of the rotary and hoist, andthe best results are obtained when the pumps are driven by individualengines.

In my present invention, an arrangement of individual engines for therotary and pumps and of a size to give an efficient use of steam duringthe rotary drilling operations, is provided and arranged so that theymay be combined to drive the hoist during the hoisting operation, and toprovide sufficient power for this latter purpose,

The engine driving the rotary must be reversible so that the rotarytable may be turned in either direction, and both engines when combinedfor hoisting must be simultaneously reversible so that the hoistclutches, which are ordinarily of the jaw type, may be disengaged.

In the usual arrangement of drilling rigs and apparatus, the rotary issituated at the center of the derrick floor and a draw-works including ahoisting drum is arranged at one side of the der rick floor. The drivingengines are outside of the derrick, generally arranged between the mudpumps, draw-Works and hoisting drums. This arrangement may also be usedin my invention and the engine for driving the rotary may be connectedto the jack shaft of the draw works and thence to the rotary, thehoisting drum being disconnected or unclutched from the jack shaft whiledriving the rotary. The engine for driving the pump is aligned, or hasits driving shaft aligned, with that of the rotary driving engine, andis provided with a clutch whereby this driving shaft may be clutched tothe shaft of the rotary driving engine, so that the power from these twoengines may be combined and transmitted to the jack shaft of thedraw-works. The rotary being disconnected or unclutched from the jackshaft, and the hoisting drum clutched to be driven from the jack shaft,the combined power of the two engines may be applied for driving thehoist. During this period the pump driving engine will be disconnectedor unclutched from the mud pump.

An embodiment of the invention is illustrated by way of example in theaccompanying drawings, in which:

Figure 1 is a diagrammatic plan view of a rotary, draw-works, enginesand pump, embodying a preferred form of the invention;

Figure 2 is a plan view of the rotary and mud pump driving engines;

Figure 3 is an elevation of the rotary and mud pump driving engines;

Figure 4 is an end view taken from the right 01' Figure 2;

Figure 5 is a plan view of a control mechanism for the engines, and

Figure 6 is a somewhat diagrammatic perspective view illustrating theunitary control mechanism which is effective to control the admission ofsteam to both engines and also the respective points of cut-off andreversal thereof.

In the embodiment of the invention shown in the accompanying drawings,an engine ill for driving a mud pump II, and an engine I2 for driving arotary, both of these engines being reversing engines, are mounted on acommon foundation, as, for example, on a pair of skids I3. The engine Iis provided with a drive shaft I4 which projects from each end of theengine. A clutch element l connected to a sprocket i6 is rotatablymounted on the outer projecting end of the shaft opposite acomplementary clutch element ll, slidably keyed on the projecting end ofthe shaft l4. When the clutch element I5 and sprocket are clutched tothe shaft i4, the engine drives the pump H through the sprocket IS, thechain l8 and a, sprocket E9 on the pump. The engine I2 is also providedwith a driving shaft which is coupled by means of a coupling 2! to aconnecting shaft 22, aligned with the shafts l4 and 2B, and carriedbetween the pair of bearings 23 and 24 on the skids l3. A clutch element25 is mounted on the end of the shaft 22 nearest the engine i 0 and isslidable to engage and clutch with a clutch element 26 on the adjacentend of the drive shaft [4. Through the above mechanism it will beapparent that the shaft i4 may clutch at one end to drive the mud pumpit and at the opposite end may be clutched to the connecting shaft 22. Acontrol lever 27 is provided to throw the clutch 25 to clutching orde-clutching position. Another clutch lever 2'l' is connected by meansof a link 28 to a clutch lever 29 engaging the clutch element ll.Consequently the engine I ll may drive either the pump l i or theconnecting shaft 22.

The rotary driving engine i2 is permanently connected or coupled to theshaft 22. The shaft 22 drives the jack shaft 31 of a draw-works 32. Forthis purpose it may be connected to the drawworks by any suitable means,as, for example, by a sprocket chain. Any suitable type of drawworks maybe employed, a two-shaft draw-works being shown in the accompanyingdrawings by way of example. In this type, the draw-works may be drivenalternatively by either one of a pair of driving chains 3! and 32 whichare trained about respective sprocket wheels 33 and 34 and keyed on theshaft 22. The chains serve to drive sprocket wheels 35 and 36respectively on the jack shaft 31 of the draw-works 30, to which thesprocket wheels may be alternatively clutched by clutches 38 and 39 todrive the jack shaft at either of two selected speeds. A sprocket wheel40 rotatably mounted at one end of the shaft 31 may be clutched to thelatter by a clutch 4i so as to drive a chain 42 which drives a rotary43. It will be apparent that the chains 3! and 32 are continuouslydriven by the shaft 22 and may be alternatively clutched to the 'shaft31, and that the shaft 31 may be clutched to the sprocket wheel 40 todrive the rotary 43 or may be unciutched therefrom. This shaft 31 may beclutched by means of a clutch 44 to a sprocket wheel 45 at the end ofthe shaft opposite the sprocket wheel 40 or may be clutched by a clutch46 to a sprocket wheel 41 intermediate the sprocket wheel 35 and thesprocket wheel 40. The sprocket wheels 45 and 41 may drive a hoistingdrum 48 alternatively through chains 49 and 50 respectively.

Through the above arrangement it will be apparent that when the clutch26 is unciutched and the clutch l1 engages the clutch element IS, theengine ID will be connected only to the mud pump H. The engine l2 maydrive the jack shaft 31 of the draw works 30 through either of thesprocket chains 3| and 32. When it alone drives the jack shaft 31 theclutch 4| may be engaged to drive the rotary 43. When th hoisting drum48 is to be driven, the clutch 4| is declutched, as is also the clutchmember l1. Clutch element 26 is clutched with the clutch element 25,whereupon both of the engines in and I2 combine to drive the jack shaft31. This jack shaft 31 may be connected to the clutches 46 or 44 todrive the hoisting drum 48, with the combined power of both of theengines l0 and 12.

The engines l0 and 52 are of sufilcient size to furnish ample power forthe pump and the rotary respectively, with an early steam cut-off andtherefore with a good steam efiiciency. When these engines are used forhoisting after the well has reached a great depth and when there is along line of drill stem or of casing to be sup- I ported and hoisted,the power required necessitates a longer supply of high pressure steamto the engine pistons, and therefore it is necessary to lengthen thecut-off to very nearly the end of the stroke of the engines.

When the two engines are combined for hoisting, suitable mechanisms areprovided for simultaneously and uniformly controlling the cut-off andthe reversing of both engines and for controlling the admission of steamto them from the drillers station which is near one end of the hoistdrum. This mechanism consists in a shaft rotatable to control the steamsupply and having a telescoping or sliding part which is connectedthrough a link to a rocking lever for controlling the cut-off and thereversing of the rotary drilling engine l2. This rocking lever isconnected through a shaft to the rock shaft on the pump engine it] sothat the two may be coupled together by means of a clutch andsimultaneously operated by the driller to obtain identical cut-offs forand reversal of both engines.

A specific embodiment of this control mechanism is diagrammaticallyshown in the accompanying drawings. Figure 6 shows the essentialelements of the control means detached from the other operating parts,in the interest of clearness. In this view a number of parts carried bythe main engine shaft are omitted for the purpose of simplicity ofillustration.

A single throttle valve 5! is adapted to control the admission of steamto both engines l0 and 12. This throttle valve has a spindle connectedto a rotatably controlled shaft 52 which telescopes into a rotatableslidable member 53 carried in a bracket 54 on a strut secured to a leg55 of the draw works or derrick 30. The outer end of the slidable member53 is provided with a.hand wheel 56 which is so mounted that it can berotated about its axis and moved longitudinally thereof, Member 53 mayalso be held in any predetermined position of longitudinal adjustment,by means of a latch 51 suitably mounted on bracket 54. Rotatab1y,mountedon the inner end of the member 53 near its connection with the shaft 52is a block 58 which prevents the longitudinal movement of the member 53.This block has an upwardly extending lug 58a to which is plvotallyconnected a link 59 which is in turn pivotally connected to a cut-off,control, and reversing lever 58 for the engine II. The block ":8 permitsrotation of the slidable element 53 on which it is rotatably mountedwithout changing its position, but it is so held on said element 53 asto move longitudinally with the latter and thereby to swing the cut-off,control and reversing lever 80 to different positions or angles asmember 53 is shifted to different axial or longitudinal positions. Thelever 68 is secured to a rock shaft 6| of engine l2 which is alignedwith a similar rock shaft 82 of engine If). Shafts GI and 62 are adaptedto be connected with one another through an intermediate shaft 63 whichis connected by a universal joint 64 with the shaft 62 and which isarranged to be coupled at will with a shaft 6| when the clutch elements65 and 66 are engaged. When the engines operate individually, the clutchelements 65 and 66 will be uncoupled, but when the two engines arecombined or coupled in tandem, the clutch elements 65 and 66 will beengaged. When so engaged. the movement of cut-off, control and reversinglever 68 will act through shaft GI and connecting shaft 63 tosimultaneously and equally shift the cut-off and reversing lever 61mounted on the shaft 62 to thereby control the cut-off of engine In orthe reversing thereof. Likewise lever 61, when rotated to an extremeposition, is effective to either change the point of cut-off or toreverse engine I independently of the operation of engine 12 at suchtimes as the clutch elements 65 and 86 are disengaged. The same is trueof the lever 60 when the clutch elements are disengaged. When the twoengines are combined or operating in tandem, it is important that thevalve control mechanism thereof be properly synchronized. The reversedrive for engine I0 is held in quadrant notches by a set screw on alever 61 in cooperative engagement with the notches as shown in Figure6, while operating the pump. This locking means is disengaged when theengines are operated in tandem, as for hoisting purposes, so that thereversing mechanism for the combined engines l8 and I2 can be instantlycontrolled from the drillers position, as shown. Synchronization isobtained by the coordination of parts described, which act in concertwith the respective reversing and cut-off mechanisms of the two engines.Each engine is equipped with the conventional form of slide valve I02]and I21; which controls the admission of steam from the steam chest ofeach engine to the cylinders thereof. The engine I0 is equipped with apair of eccentrics 10 which are connected by means of eccentric strapsshownwith the curved arouate link 12 which is slotted for slidingengagemeent with the block 74 suitably connected with the actuating rod15 of the slide valve lilo. This valve mechanism, known in the art asthe Stephenson link motion, is effective to vary the point of cut-off ofthe slide valve I01), and also, when shifted to proper position, toreverse the direction of rotation of the engine. For shifting theslotted link, the shaft carries a downwardly extended arm 18 which isconnected therewith by a member 18, as shown;

The engine I! is equipped with similar eccentrics |818,. which similarlyactuate a slotted arcuate link 18 having a block 88 for transmittingmotion to the slide valve 121: through a valve rod 8|. The link 18 ofthe valve mechanism is connected by a member 18a to a lever 82 securedto the shaft 6|. Thus the point or cutoff for engine i 2 can also bevaried or the engine can be reversed upon shifting of the shaft 8|through lever 68 to the proper angular position. From the foregoing, itwill be apparent that when the clutch elements and 68 are engaged, therespective valve mechanisms for the two engines coupled together by theclutch 28 may be operated in proper synchronismso that optimum operatingconditions will be maintained. It is advantageous, when the two enginesare operating in unison, to control the supply of steam from a singlepoint. This is effected by the steam control arrangement best shown inFigure 6.

When the engine Ill is driving the pump H, the

steam supply coming from the steam main 83 is controlled by a valve 68which is connected With a by-pass pipe 84 and also connected by a pipe85 with a pipe 86 which in turn connects the steam chests of bothengines. The valve 89 in the pipe 86 is only open when the engines arecombined to operate at tandem. During such tandem operation the valve 68will be closed. Thus the supply of steam to both engines from the main83 will be controlled by the throttle valve 5|. When the engine in isdriving the mud pump II, the steam supply is controlled through thevalve 68. At such times the valve 69 will be closed, and therefore thethrottle valve 5| will control only the engine l2.

By utilization of the unitary control mechanism shown and described, itwill be apparent that the rotary and the mud pump may be independentlydriven by their individual engines under conditions most suitable forthe efficient use of steam. When hoisting is to be done, these enginesmay be disconnected from the rotary and pump and coupled together, thenused to drive the hoisting drum. During this latter operation theircut-offs may be interconnected so that the cut-offs of both engines maybe controlled as a unit simultaneously with the control of the throttlevalves, these controls all being operable from the controllers stationnear the drawworks. Through the above invention, therefore, the steammay be utilized most efficiently during the pumping and rotary drivingoperations and be capable of furnishing the maximum power required forthe hoisting drum.

While I have described quite specifically the construction andarrangement of the parts herein shown, it is to be understood thatvarious struc tural changes may be made and rearrangements of the partsmay be resorted to without departure from the invention as defined inthe appended claims.

I claim:

1. A power plant and control mechanism therefor comprising two steamengines each adapted to independently drive separate units, means forcoupling said engines together for driving a third unit requiringgreater power than either of said units, and a unitary control mechanismfor both engines comprising a steam line connecting both engines, ashut-off valve therein, a steam supply main, respective pipes connectingsaid main with said steam line on opposite sides of said valve, athrottle valve in one of said pipes and a shut-oi! valve in the other ofsaid pipes, whereby one of the engines may be controlled by the throttlenected therewith for operating said actuating means and the throttlevalve to selectively control one or both oi said engines.

3. The combination with two steam engines valve while the other engineis independently 5 each equipped with a slide valve and each havingoperated, and permitting control of both engines by said throttle whenthe engines are coupled together.

2. A power plant and control mechanism therefor comprising two steamengines each adapted to independently drive separate units, means forcoupling said engines together for driving a third unit requiringgreater power than either of said units, and a unitary control mechanismfor both engines comprising a steam line connecting both engines, ashut-off valve therein, a steam supply main, respective pipes connectingsaid main with said steam line on opposite sides oi. said valve, athrottle valve in one of said pipes and a shut-off valve in the other ofsaid pipes, whereby one of the engines may be controlled by the throttlevalve while the other engine is independently operated, and permittingcontrol of both engines by said throttle when said engines are coupledtogether, reversing mechanisms for each of the two engines, meansoperative to actuate the reversing mechanism for the engine separatelycontrolled by the throttle valve, 9. common actuating means for bothreversing mechanisms operable when a the engines are coupled together,and means con- 30 actuating mechanisms therefor capable of reversingandvarying the point 01' cut-oil, clutching means to couple both slidevalve actuating mechanisms for simultaneous operation, an ac- 10 tuatingmember common to both valve mechanisms when said clutching means areengaged, a steam supply main, a throttle valve connected therewith, apipe connection between both engines communicating with the throttlevalve. a

1.5 shut-on valve in said pipe connection normally open when bothengines are coupled together and closed when they operate independently,a bypass pipe line from said supply main around said throttle valve andsaid shut-ofl valve, a control 1 valve in said by-pass line normallyclosed when the engines are coupled together and adapted to control theoperation of one of said engines when said shut-off valve is closed, andmanual control means operatively associated with said throttle 25 valveand said actuating member, whereby the admission oi! steam to the twoengines, the cutofis thereof, and the direction of rotation thereof arecontrollable from a single operating station upon actuation 01 saidmanual control means. AUGUST R. MAIER,

